Hydraulic apparatus



March 13, 1934. l.. F. MooDY 1,951,199

HYDRAULIC APPARATUS Original Filed May 28, 1927 2 Sheets-Sheet l March 13, 1934. L.. F. MOODY HYDRAULIC APPARATUS Original Filed May 28, 1927 2 Sheets-Sheet 2 INV NTORA ATT . Vation above tailwater.

Patented Mar. 13, 1934 HYDRAULIC APPARATUS Lewis Ferry Moody, Philadelphia, Pa.

Original application May 28, 1927, Serial No.

Divided and this application August 2, 1930, Serial No. 472,548

18 Claims.

This invention relates to hydraulic turbines and particularly to those of the vertical shaft type.

In the eiiort to increase the speed of a turbine under a given head, so as to permit a reduction in the size of the generator driven by the turbine as well as the size of the turbine itself and the accompanying power house structure, runners having extremely high values of specific speed have been developed, but these necessarily require the location of the runner at a low point with respect to tail water. As hereinafter explained in detail, the higher the specic speed the lower the runner must be placed with respect to tailwater, and conversely the higher the runner is placed with respect to tail water, the lower will be its permissible specific speed. With the high specific speed runner lo'cated at the required low point there is, in many plants, available space above the runner for the location of a second runner connected with the same shaft which if it could be added to the unit would materially increase the power output and consequently the total specic speed of the entire unit.

The object of my invention is to provide a turbine in which this space above the lower runner contains an auxiliary upper runner mounted on the same shaft with the lower runner and so combined therewith that the lower runner may have a high specific speed while at the same time the auxiliary upper runner is adapted to operate at a lower specific speed suitable for its higher ele- The fact that runners of different specic speed are adapted to operate normally at the same actual speed permits the two runners to be mounted on the same shaft. In this way the high specic speed of the lower runner is maintained, and at the same time additional power is efliciently generated and delivered to the shaft by the lower specific speed upper runner, thus i-ncreasing the specic speed oi the turbine unit as a whole.

The double runner turbines of the prior art are unable to operate most efficiently because there is mounted on the saine shaft at least two substantially identical runners, which are therefore suited only for the same elevation and specic speed. For reasons which will be apparent hereinafter these prior runners are designed for the lower specific speed conditions under which the upper runner operates, thus eliminating cavitation of the upper runner and permitting it to operate eiiiciently although this is done at the expense of limiting the output of the lower runner. The total specific speed of the prior units will, therefore, be .the resultant of two identical runners each having a specific speed limited to suit the elevation of the upper runner. If the runners were identically designed toV have a high specic speed in accordance with the elevation of the lower runner and thereby cause the lower runner to operate efficiently, then the runner would necessarily be unfit for operation at the elevation oi the upper one dueto cavitation and ineciency of operation. Hence it is seen that if both runners are designed for the conditions of the lowermost runner the upper runner is subjected to prohibitive conditions while if both runners are designed for 'the conditions of the uppermost runner then the lower runner is subjected to unnecessary limitation of its power. Thus, these prior double runners have not combined in a single unit the feature of the highest possible specic speed along with proper operation of both runners as is made possible with my pres- {5} ent invention.

I here present the principle that these disadvantages can be obviated, and that in a single turbine unit an upper runner may be used to increase the power, or for the same total power the actual speed of the unit may be increased, by applying runners of different form and capacity so that the upper runner will vbe of relatively less power and less specific speed and the lower runner of relatively greater power and greater specic speed, but both will be keyed to the same shaft and will run at the same actual speed.

Further objects of my invention in the form and cooperation of the turbine parts will appear from the following description taken in connection with the accompanying drawings, in which Fig. 1 is a vertical sectional elevation of -a turbine unit embodying the invention', taken on line 1-1 of Fig. 2; Y

Fig. 2 is a horizontal view on line 2-2 of Fig. 1. 9154 In the embodiment of the invention shown in Figs. 1 and 2l the flow from headwater enters the turbine through intake 10 in spiral form, passing the water with a whirl through Xed stay vanes 16 and adjustable guide vanes 17 to the transi- 10'0 tion space 17 between the upper runner 14 and thev lower runner The flow is guided into the two runners by the double conical distance piece or sleeve and is discharged, usually with a whirl, upward into the draft tube 11 and down- 105 Ward into the draft tube 12, both of these tubes being of the annular spreading type adapted to convert the velocity Ihead of bothl the meridian and tangential, velocity components into pressure head. The draft tubes 11, 12, discharge through 11-0 outlet passages 13 into tail water having its level indicated at t.

The runners 14, 15 are of the highfspecic speed propeller type, the upper runner 14 being smaller in diameter and of less power than the lower 1:15 runner 15A and accordingly of lower specific' speed than the lower runner. The unit shown is adapted to'develop9500'horsepower at 200 R. P. M. and a head of 40 feet. The throat of the lower runner islocated atA 4f 9 below tail water so that the 120 stiAll velocity head regained in the draft tube plus a factor to cover local cavitation, plus the static draft head will equal rthe barometric pressure corresponding to 32.83 feet water column. As thus installed the lower runner 15 will develop about 6000 of the total 9500 horsepower and its specific speed will be about 154. The upper runner 14 at the same actual speed Will have a specific speed of about 118 and will develop approximately 3500 horsepower determined by the total draft head acting upon it at the throat, said draft head being computed as above indicated as the sum of the static draft head plus the velocity head regained in the draft tube, plus the factor to cover local cavitation. This total should not exceed 32.83 feet.

One of the principles underlying this invention is thus the relation between the elevation of the turbine runner with respect to tail water, the effective head on the runner and its specific speed. As the design of a runner is progressively modified to increase its specific speed, the velocity head of the water passing through it continuously increases and represents an increasing fraction of the effective head. Assuming that the runner will be equipped with an efficient draft tube capable of regaining a large proportion of the velocity head discharged therefrom, the height at which the runner may be located with respect to tail Water becomes more and more limited, requiring it to be placed at continuallyT lower elevations, as the specific speed increases. In addition however to this allowance for velocity head based on the average velocity of the stream passing through the runner, a seco-nd factor must also be considered, namely, what I have termed local cavitation, or local pressure reduction. The static pressure existing within the runner is not constant throughout the entire Waterway but varies from the periphery toward the axis of the runner and also varies across each bucket from the face of one vane to the back of the next vane and there is therefore a local reduction of pressure at some points of the runner causing this local pressure to be a considerable amount below the average pressure in the entire waterway. This local pressure reduction may be expressed as the product of a coefficient multiplied by the effective head. This coefiicient varies somewhat depending on the peculiarity of the individual runner design, but in general it increases with the specific speed of the runner, and for a runner of any given design characteristics, this coefficient must increase if the specic speed is increased.

A curve may be drawn showing the functional relation between this coefficient and the specific speed. Such a curve will represent the general effect of specific speed for runners of usual characteristics and show graphically how the coefficient of cavitation increases with an increase in specic speed. In designing any turbine installation, the specific speed selected for the runner must be such that at a given elevation of the runner with respect to tail water, the sum of the static elevation of the runner above tail water plus the amount of velocity head regained in the draft tube, plus the product of the cavitation coefiicient-cc*multiplied by the effective head must not exceed the barometric pressure head; that is, substantially the pressure head of the atmosphere.

It follows that if a runner of a given specific speed is placed too high above tailwater so that the absolute pressure at a local point within the turbine approaches too close to the vapor pressure of Water, the water may part from the vane surfaces leaving a cavity filled with vapor, and at such points pitting or corrosion of the metal is likely to occur as well as vibration and a possible impairment of the power and efficiency.

If hs is the elevation of the runner throat or point of minimum diameter of the turbine passage above tail water; hb the barometric head corresponding to the temperature of the water and altitude of the location (corresponding to atmospheric pressure minus vapor pressure of the water) H, the effective head on the turbine; and

Ns, the specific speed of the runner, then an approximate empirical relation may be found such that the absolute pressure at any local point within the turbine will not fall below the vapor pressure of the water for turbines of normal characteristics for various specific speeds.

From the available data representing the experience in existing plants, the effects of regained velocity head in the draft tube and the local pressure reduction within the turbine may be combined and expressed as a function of the specinc speed. By this method, it is found that in order to provide a proper safeguard against cavitation a specic speed should be selected in relation to elevation above tailwater and effective head in accordance with a formula of the following general form:

For turbines of the Francis type- For turbines of the propeller type The coefficients of 125 and 150 are of course dependent upon the particular designV characteristics, but the above round figures are sufficient for runners of usual design to provide a general guide in making preliminary calculations. In actual turbine design, the separate effects of cavitation and velocity head regain may be denitely caiculated for the particular design and any necessary correction then made in the specific speed or elevation of runner above tailwater.

In a multi-runner vertical shaft turbine Where the separate runners must be placed at dierent elevations, the above formulas will serve as a basis for calculating the power capacity which can be safely assigned to each individual runner using in the case of each runner its own individual elevation hs above tailwater. Since however the runners are all keyed to the same shaft and must therefore have the same absolute speed of rotation, the horsepower capacities will vary according to the following relation:

For Francis turbines- HW HP: 15,600 W (hb-hs) For propeller type turbines- H'/2 HP: 22,500? (hb-hs) in which N equals the revolutions per minute of the shaft.

The functional relations represented by these formulas are shown on Fig. 8 in which the horsepower capacities of individual runners are plotted for a standard speed of 100 R. P. M. and for heads of 20, 4:0 and 60 feet in relation to the '.tailwater. 'The hcrserx'iw'erA for an'yfthersped 'can' bei found by"multiplying y the horsepower at Y 1'00l R. P. 1M.;fde'notedffb'y that is, if we taken an-elevationfatY a heightfabove '.tail'water' equal to the barometric headjwhichat :ordinary temperatures and altitudes may 'be taken asapproximately 32feet,then the horse- Ypowers/of a series ofrunners=-at'diierentelevancsu-199 "elevationfof the individual runner vvwith'respect'to "posinglv the' upper or""auiztliary runnerfj'l'cnfthe 2 (HP rooN),l by

:horsepowers v'of individual runners atflconstant speedand 'the runnerelevations is alinarfo'ne,

tions keyed to the same 'shaftwill' be veryfnearly proportional to theirfvertical distance below`- this V'32'foot/elevation when "the runners are of the plotted on' this chart' are straight lines radiating 'from a point at 32 feet elevation `ontheyertical Vaxisof thechart. differentslope of linemustbe-used for turbines peller type.

same general type. vTherefcre,"all ofv thegraphs It will also be'notedthat a of'Francis type from that required by the pro- Therefore, the 'conditions in somefcases will fcall for the lower runner of a'multi-runnerverpticallshaft turbine to'b'e of a'different` type from the upper runner. "For example, in a` turbine for Ailfeet head if'the upper'run'ner must'be placed higherthan about ve feet above tailwater,` the Vconditionsvfor thisupp'er runner would not -be suitableffor'a propeller runner ofusual characteri'stics according to `present practice, and a Francis type "runner would then'oe 'selected for lthe 'uppe'r runnerof such a unit. :In'a unitfor such'con'ditions, thelower lrunnensetat alower elevation, could be of the propeller type and could therefore have 'av very much greaterv 'capacity vthan jthe upper' runner.

Ifin the above'formulas,'thefquantity ris-'Lbs lis 'c'alle'dthe absolute static drafthead, 'thenut follows"that the power capacities fa `seri'esof l'runners"mounted on acommon shaft shouldibe appro'xirnately proportional to their individual absolute Ystatic-draft heads when the runners are 'of similar type.

-By thus combining *with the flower "runner vtlie upper runner of less'power'fandfof lwerspecic speed, thepower output is greatlyincreased and the same actual speed of rot'atio'nlis maintained.

increased by over one-half to attain a totaloutputof 9500V To attainthis 'samehor'sepower in a single runner at the 'saine :head and same actual speed, 'the specic 'speed of Athe unitw'ould would be 193.5 and the runner should be placed about seventeen feet below'tailw'ater in order 'to :keep the total draft head vofthe. unit'equal to or less than 32.83. With this high specic speed a runner would be yused that would develop "a maximum efciency considerably vlower than 'the total efciency of "the combined unit of lFigsl and 2. The single runner unit, v'due to lthe Vhigh negative static draft head, would also require VVa much deeper excavation than the double unit. On the other hand, if the same specific Speed were used for the single 'runner unit as in Ythe lower runner of the unit shown, the actual speed would be materially reduced, theeiciency some.- what lower, and the sizeof Vthe runner and of Vthe whole unit considerably greater.

The "new results of my ,invention Aare attained in the turbine of Figs. 1 and 2 simply by interyon'dthe upperguide-bearing 23'i`n draft tube cone 24, a lowerguide be'aringj'25"is 'of Vmy copending applications, Serial `Nos,- 553,294

generator 22, and providing this runnerMwi-thjf'the supply and discharge passages for the liiow Y through" it. This involvessimply -alengthening `80 `f "the entrance iguide Y Y n Of the W passage 'and cist'htge- Olltltpssge Afor the upper 'runner. Acontihuous col'ufar *supportis'pro-v'dedlfrom thesub-foundatin'to ,V

l'varies and jvthe pr'vi'sin the outer wall of the upper draft tube as a-reaber/e. y

IDue to the large overhang'of the shaft'21beremovable 95 added in the lower draft tube'con'e 26,-tlfese1bearings being supplied with'lubricantthrough-pipe connections 27 and 28. I,

The'singlefring of guide'vanes 171s'ervI-n'g yfor ib() both'runners is operated' byy submerged operati-ng `mechanisrn comprising ring 40 'and linksl'b'etween the ring and vanes, the'ring being-con'- nected by'reach'rods 18 and rocker arm43 tobe -turned` by the vertical shaft 42-from power means l'f05 'controlled by the governoron the power Avhouse If a single runner were employed under Lthe same conditions as the 'double runner,V there would be requ'red a 'considerablylarger'throat l'm diameter'than eitherof the'runnersin vthe two- 'much Ylarger' than either Vof the two -runners shown.

lTo `accomplish this difference in specic :speedi'jzo between the upper and lowerrunnersand-also to Vobtainfurtheradvantages one or both of the runners, but preferably vthe'upper runner, can beof the adjustable blade type suchasshown'ineither and 631,985, filed vrespectively -April j15, 1922 land `April'll, 1923. The invention `is thus not limited to any particular type of runner. Since the actual speed of all runners must be the sameto permit `their being keyed to the same shaft, the lower specicspe-ed Vof the upper runner necessarily requires thatjit shall have lower horsepower capacity and quantity of discharge than the lower one. The resulting combination produces a unit which-is higher Ain the effective speed'of the unit than can be produced ether by a single run, vner or by a multi-runner unit Yhavingrunne'rs of identical-size and design. v l I This'application isa vdivision of applicationled May 28, 1927, now patent No. 1,776,391, issued 51546 September 23, 1930 and is directed particularly -to the modification shown herein wherein the water ows to one runner in lone direction and lto the other `runner in a direction away from the rst direction, although it will of course be, unL der'stood that there are other features of the n*- vention as covered by the 1appended claims.

It will of course be understood by those skilled in the art that from the foregoingdesoription and 'illustrations of -Various modifications that 'various sigo 'tifa rchanges may be made without departing from the xsprit of the invention as set forth in the appended claims.

I claim: l. In a hydraulic turbine the combination with a single shaft, of a plurality of runners thereon at different elevations, the upper one of said runners being of smaller diameter than the lower runner, said runners having different specific speeds and being adapted for the same actual :speed during simultaneous normal operation, and

.runners of different specic speeds and power Voutput and adapted for the saine actual speed during simultaneous normal operation, the upper one of said runners being of smaller diameter than the lower runner, a common transition space for said runners and a single set of guide vanes for directing the flow to said runners.

3. In a hydraulic turbine a central intake passage, a divided discharge passage, a plurality of runners having the same acuual speed while being simultaneously normally operative but of different specic speeds and power output, said runners being spaced from each other on a vertical shaft and the upper runner being of smaller diameter than the lower runner, a common transition space for said runners and a single set of guide vanes for directingr the flow to said runners.

4. In a hydraulic turbine an intake 1passage, a discharge passage, a vertical shaft, a runner on said shaft located below tailwater, a second runner on said shaft located above tailwater of smaller specific speed and power output than the rst mentioned runner whereby the upper runner is smaller in diameter than the lower runner, said runners being adapted for the same actual speed during simultaneous normal operation and being spaced apart from each other by a conical distance piece which is adapted to divide the inflow and direct it to both of said runners.

5. In a hydraulic turbine a central intake passage, a vertical shaft, a runner on the lower end of said shaft receiving the flow downwardly from said intake, a second runner of diierent specific speed and power output spaced on said shaft above said first mentioned runner and receiving the flow upwardly from said intake, said runner on the lower end of said shaft being of larger diameter than said second runner and both of said runners being adapted for the same actual speed during simultaneous normal operation, a common transition space between said runners and a discharge passage receiving the flow from both of said runners.

6. In a hydraulic turbine, the combination comprising an intake passage, a discharge passage, a vertical shaft, a runner on said shaft located below tailwater, a second runner on said shaft located above tailwater and being of lower specific speed and power output than the rst mentioned runner, said second runner being of smaller diameter than said other runner and both of said runners being adapted for the same actual speed during simultaneous normal operation and being spaced from each other by a curved distance piece forming an inner boundary of a transition space adapted to divide the inflow and direct it to both of said runners.

7. In a hydraulic turbine, the combination comprising a single vertically disposed shaft, a

being of smaller diameter than the lower run-k ner, and means whereby iluid ows to one runner in one direction and to the other runner in a' direction away from the first direction.

8. In a hydraulic turbine, the combination comprising a single vertically disposed shaft, a plurality of runners thereon at diierent elevations and having different specic speeds adapted to permit simultaneous normal operation, at the same actual speed, and said uppermost runner being ofsmaller diameter than a lower runner, and means whereby the degree of whirl in the flow to each runner may be varied.

9. In a hydraulic turbine, the combination comprising a single shaft, a plurality of runners thereon at different elevations and having different specic speeds adapted for simultaneous normal operation at the same actual speed, whereby an upper one of said runners is of smaller diameter than a lower runner, means whereby whirl may be imparted to the flow to each run-Vl ner, and means whereby the degree of whirl to each ruimer may be simultaneously adjusted.

10. In a hydraulic turbine, the combination comprising a single vertically disposed shaft, a plurality of runners thereon at diierent elevations and having diiferent specific speeds adapted for simultaneous normal operation at the same actual speed whereby an upper one of said runners is of smaller diameter than a lower runner, means forming a common transition space between said runners, and an entrance passage communicating with said transition space and lying within substantially the same plane as said space. Y i 1l. A hydraulic turbine comprising, in combination, a single vertically disposed shaft, a plurality of runners disposed thereon at different elevations and having different specific speeds adapted to have simultaneous normal operation at the same actual speed whereby an upper one of said runners is of smaller diameter than a lower runner, means forming a common transition space between said runners, and a volute inlet passage communicating with said transition space around its entire circumference whereby the fluid flows from said volute passage to said space in a radially inward direction and then divides and flows in opposite directions to said runners.

l2. A hydraulic turbine comprising, in combination, a single vertically disposed shaft, a plurality of runners disposed thereon at different elevations and having different specic speeds adapted to permit simultaneous normal operation at the same actual speed whereby an upper one of said runners is of smaller diameter than a lower runner, means forming a common transition space between said runners, a volute inlet passage communicating with said transition space around its entire circumference whereby the fluid flows from said volute passage to said space in a radially inward direction and then divides and ilows in opposite directions to said runners, and means adapted to impart whirl to the flow which passes into said transition space.

13. A hydraulic turbine comprising, in combination, a single vertically disposed shaft, a plurality of runners thereon of different specific speeds and adapted for simultaneous normal operation at the same actual speed whereby an upper one of said runners is of smaller diameter than a lower runner, means forming a common transition space between said runners, separate flow decelerating draft tubes for each runner, and means forming connecting passages leading from said draft tubes into a common tailrace passage with the inner walls of said connecting passages defining a tapered formation.

14. A hydraulic' turbine comprising, in combination, a single vertically disposed shaft, a plurality of runners thereon of different specific speeds and adapted for the same actual speed during simultaneous normal operation whereby an upper one of said runners is of smaller diameter than a lower runner, means forming a common transition space between said runners, separate flow decelerating draft tubes for each runner, and means forming connecting passages leading from said draft tubes into a common tailrace passage with the inner walls of said connecting passages defining a tapered formation in a downstream direction when viewed in vertical section.

15. A hydraulic turbine comprising, in combination, a single vertically disposed shaft, a plurality of runners thereon having different specific speeds and adapted to have simultaneous normal operation at the same actual speed whereby an upper one of said runners is of smaller diameter than a lower runner, means forming a common transition space between said runners, a separate flow decelerating draft tube for each runner, collector passages surrounding said draft tubes and discharging in a downstream direction, and means forming passages for connecting the collector passages with a common tailrace passage, the upstream walls of said connecting passage defining a tapered formation in a downstream direction when Viewed in vertical section.

16. A hydraulic turbine comprising, in combination, a single vertically disposed shaft, a plurality of runners thereon having different specific speeds adapted for the same actual speed during simultaneous normal operation whereby an upper one of said runners is of smaller diameter than a lower runner, means forming a common transition space between said runners, separate flow decelerating draft tubes for each runner of substantially similar form, collector passages surrounding said draft tubes and extending downstream and means forming a passage for connecting the collector passage with a common tailrace passage, the upstream walls of said connecting passage defining a tapered formation in a downstream direction when viewed in vertical section.

17. A hydraulic turbine comprising, in combination, a single vertically disposed shaft, a plurality of runners thereon of different specific speeds and adapted for the same actual speed during simultaneous normal operation whereby an upper one of said runners is of smaller diameter than a lower runner, means forming a common transition space between said runners, and draft tubes, one leading from each runner in opposite directions, each draft tube having smoothly curving inner and outer walls formed as surfaces of revolution.

18. A hydraulic turbine comprising, in combination, a single vertically disposed shaft, a plurality of runners thereon of different specific speed and adapted for the same actual speed during simultaneous normal operation whereby an upper one of said runners is of smaller diameter than a lower runner, means forming a common transition space between said runners, and draft tubes, one leading from each runner in opposite directions, the inner wall of said transition space being in the form of a smoothly curving double ended conical member whose surface merges with the hubs of said runners.

LEWIS FERRY MOODY. 

